Torque reaction pulley for an inertia cone crusher

ABSTRACT

A torque reaction pulley for an inertia cone crusher having an elastically deformable component responsive to a change in torque through the drive transmission of the crusher due to rotation of an unbalanced weight within the crusher.

FIELD OF INVENTION

The present invention relates to a torque reaction pulley positionablewithin the drive transmission of an inertia cone crusher and inparticular, although not exclusively, to a torque reaction pulleyconfigured to dissipate changes in torque created by the rotation of anunbalanced mass body within the crusher.

BACKGROUND ART

Inertia cone crushers are used for the crushing of material, such asstone, ore etc., into smaller sizes. The material is crushed within acrushing chamber defined between an outer crushing shell (commonlyreferred to as the concave) which is mounted at a frame, and an innercrushing shell (commonly referred to as the mantle) which is mounted ona crushing head. The crushing head is typically mounted on a main shaftthat mounts an unbalance weight via a linear bushing at an oppositeaxial end. The unbalance weight (referred to herein as an unbalancedmass body) is supported on a cylindrical sleeve that is fitted over thelower axial end of the main shaft via an intermediate bushing thatallows rotation of the unbalance weight about the shaft. The cylindricalsleeve is connected, via a drive transmission, to a pulley which in turnis drivably connected to a motor operative for rotating the pulley andaccordingly the cylindrical sleeve. Such rotation causes the unbalanceweight to rotate about the a central axis of the main shaft, causing themain shaft, the crushing head and the inner crushing shell to gyrate andto crush material fed to the crushing chamber. Example inertia conecrushers are described in EP 1839753; U.S. Pat. No. 7,954,735; U.S. Pat.No. 8,800,904; EP 2535111; EP 2535112; US 2011/0155834.

However, conventional inertia crushers whilst potentially providingperformance advantages over eccentric gyratory crushers, are susceptibleto accelerated wear and unexpected failure due to the high dynamicperformance and complicated force transmission mechanisms resulting fromthe unbalanced weight rotating around the central axis of the crusher.In particular, the drive mechanism that creates the gyroscopic precisionof the unbalanced weight is exposed to exaggerated dynamic forces andaccordingly component parts are susceptible to wear and fatigue. Currentinertia cone crushers therefore may be regarded as high maintenanceapparatus which is a particular disadvantage where such crushers arepositioned within extended material processing lines.

SUMMARY OF THE INVENTION

It is an objective of the present invention to provide a drivetransmission coupling mountable at an inertia crusher to form part of adrive transmission mechanism for rotational drive of an unbalancedweight being configured to dissipate relatively large dynamic torqueinduced by the unbalanced weight gyrating within the crusher and toprevent the transmission of such torque to the crusher and in particularthose components of the drive transmission.

It is a further specific objective to provide an inertia crusher drivetransmission coupling configured to deflect and/or dissipate mechanicalloading torque associated with the oscillating movement of theunbalanced weight that would otherwise lead to accelerated wear, damageand failure of component parts of the drive transmission and/or thecrusher generally.

The objectives are achieved by a drive transmission coupling in the formof a pulley compatible with a drive transmission arrangement ormechanism of an inertia cone crusher that, in part, isolates therotating unbalanced weight and in particular the associated dynamicforces (principally torque) created during operation of the crusher fromat least some components or parts of components of the upstream drivetransmission being responsible to induce the rotation of the unbalancedmass body. In particular, the present drive pulley comprises a torquereaction elastic component configured to receive changes in the torqueat the drive transmission (referred to herein as a ‘reaction torque’)created by the unbalanced weight as it is rotated about a gyration axisand to supress, dampen, dissipate or diffuse the reaction torque andinhibit or prevent direct transmission into at least regions of thedrive transmission components.

The reaction torque pulley is advantageous to support the mass body in a‘floating’ arrangement within the crusher and to allow and accommodatenon-circular orbiting motion of the crusher head (and hence main shaft)about the gyration axis causing in turn the unbalanced weight to deviatefrom its ideal circular rotational path. Accordingly the drivetransmission components are partitioned from the torque resultant fromundesired changes in the angular velocity of the unbalanced weightand/or changes in the radial separation of the main shaft and the centreof mass of the unbalanced weight from the gyration axis. Accordingly,the drive transmission, incorporating the present torque reactioncomponent, is isolated from exaggerated and undesirable torque resultingfrom the non-ideal, dynamic and uncontrolled movement of the oscillatingmass body. The torque reaction coupling is configured to receive, storeand dissipate energy received from the motion of the rotating mass bodyand to, in part, return at least some of this torque to the mass body asthe reactive coupling displaces and/or deforms elastically in positionwithin the drive transmission pathway. Such an arrangement isadvantageous to reduce and to counter the large exaggerated torque so asto facilitate maintenance of a desired circular rotational path andangular velocity of the unbalanced mass about the gyration axis.

The present torque reaction pulley provides a flexible or non-rigidconnection to the unbalanced weight to allow at least partialindependent movement (or movement freedom) of the unbalanced weightrelative to at least parts of the drive transmission such that the drivetransmission has movement freedom to accommodate dynamic torsionalchange. In particular, the centre of mass of unbalanced weight is freeto deviate from a predetermined (or ideal) circular gyroscopicprecession and angular velocity without compromising the integrity ofthe drive transmission and other components within the crusher. Thepresent pulley is advantageous to prevent damage and premature failureof the crusher component parts and in particular those parts associatedwith the drive transmission.

According to a first aspect of the present invention there is provided atorque reaction pulley mountable at an inertia crusher to form part of adrive transmission mechanism for rotational drive of an unbalanced massbody within the crusher comprising a drive input portion connectable toa motor to provide rotational drive to the pulley; a drive outputportion connectable to the mass body to transmit the rotational drive tothe mass body; an elastic component formed non-integrally with the inputand output portions and having a first part anchored in coupledconnection with the drive input portion and a second part anchored incoupled connection with the drive output portion so as to be positionedin the drive transmission pathway intermediate the drive input andoutput portions; the elastic component configured to transmit a torqueto the mass body and to dynamically displace and/or deform elasticallyin response to a change in the torque resultant from rotation of themass body within the crusher so as to dissipate the change in the torqueat the crusher.

The torque reaction pulley is configured to deflect and/or dissipateexclusively mechanical loading torque associated with the oscillatingmovement of the unbalanced weight (due to deviation of the main shaftform the ideal circular path) within the drive transmission, the driveinput component or the mass body. That is, the torque reaction pulley ispositioned and/or configured to respond exclusively to torsional changeand to be unaffected by other transverse loading including in particulartensile, compressive, shear and frictional forces within the drivetransmission. Reference within the specification to ‘a torque reactionpulley’ encompasses a wheel drive transmission positioned as a driveinput component downstream (in the drive transmission pathway) of adrive belt (such as V-belts), a motor drive shaft, a motor or otherpower source unit, component or arrangement positioned upstream from thecrusher.

Reference within this specification to the elastic component beingconfigured to ‘displace and/or deform elastically’ encompasses theelastic component configured to move relative to other components withinthe drive transmission and/or the other components or regions of thetorque reaction pulley and to displace relative to a ‘normal’ operationposition of the elastic component when transmitting driving torque tothe mass body at a predetermined torque magnitude without influence orchange in the torque resultant from changes in rotational motion of thecrusher head about the gyration axis (e.g., a change in the tilt angleof the crusher head) and/or a rotational speed of the crusher head. Thisterm encompasses the elastic component comprising a stiffness sufficientto transmit a drive torque to at least part of the mass body whilstbeing sufficiently responsive by movement/deformation in response tochange in the torque at the drive transmission, the mass body or driveinput component. The term ‘dynamically displace’ encompasses rotationalmovement and translational shifting of the torque reaction coupling inresponse to the deviation of the main shaft from the circular orbitingpath.

Preferably, the torque reaction coupling is mechanically attached,anchored or otherwise linked to the drive transmission, and inparticular other components associated with the rotation drive impartedto the crusher head, and comprises at least a part or region that isconfigured to rotate or twist about an axis so as to absorb the changesin torque. Preferably, at least respective first and second attachmentends or regions of the torque reaction coupling are mechanically fixedor coupled to components within the drive transmission such that atleast a further part or region of the torque reaction coupling(positionally intermediate the first and second attachment ends orregions) is configured to rotate or twist relative to (and independentlyof) the static first and second attachment ends or regions.

The term ‘change in rotational motion of the crusher head’ encompassesdeviation of the crusher head, from a desired circular orbiting pathabout the gyration axis. Where the crusher head is inclined at a tiltangle, the change in rotational motion of the crusher head may comprisea change in the tilt angle. Optionally, the crusher head may be alignedparallel with a longitudinal axis of the crusher such that the deviationfrom the circular orbiting path is a translational displacement. Thereference herein to a ‘change in the rotational speed of the crusherhead’ encompasses sudden changes in angular velocity of the head andaccordingly the mass body that in turn results in inertia changes withinthe system that are transmitted through the drive transmission andmanifest as torque.

Optionally, the torque reaction pulley is positioned immediately belowthe crusher and represents an end drive transmission component of thecrusher positioned downstream of a drive input arrangement such as abelt drive. Optionally, the torque reaction coupling is aligned so as tobe positioned on the longitudinal axis extending through the crusherhead and/or main shaft when the crusher is non-operative or immobile.Preferably, the torque reaction coupling is positioned on the centrallongitudinal axis of the crusher such that the axis of the pulley iscoaxial with the crusher longitudinal axis.

Preferably, the elastic component is attached to the drive input andoutput portions of the torque reaction pulley via releasable attachmentssuch that the elastic component may be mounted and decoupled from thedrive input and output portions and hence the crusher. The releasableattachments may comprise bolts, screws, pins, clips, cooperatingthreads, push-fit or snap-fit connections to allow releasable mountingof the elastic component at the pulley.

Preferably the elastic component is mounted at one end of the pulley.Preferably, the elastic component is mounted at a lower end of thepulley when the pulley is secured in position at the crusher.Preferably, the releasable attachments that connect the elasticcomponent to the pulley are accessible from below the pulley tofacilitate mounting and demounting of the elastic component duringservicing, maintenance or to change the torque reaction characteristicof the pulley. In particular, and preferably at least parts of theattachments are positioned externally at the pulley.

Optionally, the drive transmission within which the present torquereaction pulley is positioned comprises at least one further drivetransmission component coupled between the mass body and the drive inputcomponent to form part of the drive transmission. Optionally, thefurther drive transmission component may comprise a torsion rod, driveshaft, bearing assembly, bearing race, torsion bar mounting socket orbushing connecting the unbalanced weight to a power unit such as amotor.

Optionally, the torque reaction pulley comprises a modular assemblyconstruction formed from a plurality of component parts in which aselection of the component parts are configured to move relative to oneanother.

Optionally, the elastic component is connected indirectly to the outputportion via at least one drive component forming a part of the pulleyand configured to transmit the torque.

Optionally, the elastic component is connected indirectly to the inputportion via at least one drive component forming a part of the pulleyand configured to transmit the torque. The drive component may comprisebearings, bearing housings, adaptor shafts, flanges, bearing races orother annular bodies or linkages that form a modular component part ofthe pulley coupling adjacent components.

Preferably the drive input portion comprises an annular belt supportcomponent to mount and positionally support a belt drive to extend atleast partially around the belt support component. Preferably, the beltsupport comprises a plurality of grooves extending circumferentiallyaround the support and recessed into an external facing surface of thesupport with each groove configured to at least partially accommodate aV-belt drive component. Preferably, the grooves comprises a V-shapedcross-sectional profile and extend 360° around the belt support.

Preferably the drive output portion comprise a race having an axiallyextending socket or recess capable of mounting one end of a torsion baror drive shaft demountably connectable to the pulley. The racepreferably comprises a plurality of bores extending internally throughat least part of the body of the race to receive attachment bolts toreleasably mount the elastic component to the race.

Optionally, the pulley comprises a first adaptor flange coupled betweenand connecting the input portion and the elastic component. Optionally,the pulley further comprises a second adaptor flange coupled between andconnecting the output portion and the elastic component. Preferably, thefirst and second adaptor flanges are resiliently deformable. Preferably,the adaptor flanges are annular and comprise respective elastomericrings.

Preferably, the elastic component comprises at least one elastomericcomponent configured to twist in response to the transmission of thetorque through the pulley. Such a configuration is advantageous as theelastic component is configured to deform in response to a change intorque through the pulley and to return elastically to the shape,configuration and position of the component prior to the change intorque.

Optionally, the elastic component comprises at least one disc havingspokes configured to deform via twisting about a rotational axis of thepulley in response to transmission of the torque through the pulley.Preferably, the elastic component comprises a plurality of discs stackedon top of one another via interconnecting members such that the spokesare arranged in series in the drive transmission pathway intermediate tothe drive input and output portions.

Optionally, at least some of the discs of the stack may be connectedaxially to adjacent discs via connections positioned towards the radialperimeter of the discs and at least some of the discs of the stack maybe connected axially to adjacent discs via mountings positioned atradially inner regions of the discs. Optionally, the stack of discs maycomprise a first attachment plate secured to an upper disc at an upperend of the stack and a corresponding second attachment plate secured toa lower disc at a lower end of the stack. Optionally, the discs may besecured to one another via bolts, pins or lugs at either the radiallyouter or inner portions.

Optionally, the elastic component comprises a spring. Optionally, thespring is a helical or coil spring. Optionally, the spring comprises anyone or a combination of the following: a torsion spring, a coil spring,a helical spring, a gas spring, a torsion disc spring, or a compressionspring. Optionally, the spring comprises any cross-sectional shapeprofile including for example rectangular, square, circular, oval etc.Optionally the spring may be formed from an elongate metal strip coiledinto a circular spiral.

Optionally, the elastic component comprises a torsion bar, pad or bodyconfigured to twist about a central axis in response to differences intorque at each respective end of the elastic component.

Optionally, the torque reaction pulley comprises a plurality of elasticcomponents such as springs of different types or configurations and/orelastomers mounted at the pulley in series and/or in parallel.

Optionally, the spring comprises a stiffness in range 100 Nm/degrees to1500 Nm/degrees. Optionally, the spring comprises a damping coefficient(in Nm·s/degree) of less than 10%, 5%, 3%, 1%, 0.5% or 0.1% of thestiffness depending on the power of the crusher motor and the mass ofthe unbalanced weight. Such an arrangement is advantageous to enable thespring to transmit a drive torque whilst being sufficiently flexible todeform in response to the reaction torque. In particular, the elasticcomponent(s) may be configured to twist between respective connectionends by an angle in the range +/−45°. Accordingly, the elastic reactioncoupling is configured to twist internally (with reference to itsconnection ends) by an angle up to 90° in both directions. Such a rangeof twist excludes an initial deflection due to torque loading when thecrusher is operational and the flexible coupling is acted upon by thedrive torque. Such initial preloading may involve the couplingdeflecting by 10 to 50°, 10 to 40°, 10 to 30°, 10 to 25°, 15 to 20° or20 to 30°. Advantageously, the elastic coupling is capable of deflectingfurther beyond the initial torsional preloading so as to be capable of‘winding’ or ‘unwinding’ from the initial (e.g., 15 to 20°) deflection.Optionally, the torsion responsive coupling comprises a maximumdeflection, that may be expressed as a twist of up to 70°, 80°, 90°,100°, 110°, 120°, 130° or 140° in both directions. Optionally, thecoupling may be configured to deflect by 5 to 50%, 5 to 40%, 5 to 30%, 5to 20%, 5 to 10%, 10 to 40%, 20 to 40%, 30 to 40%, 20 to 40%, 20 to 30%,10 to 50%, 10 to 30% or 10 to 20% of the maximum deflection in responseto the ‘normal’ loading torque transmitted through the coupling when thecrusher is active optionally pre or during crushing operation.

The deviations from the circular orbiting path of the mass body mayaccordingly result from deviations by the crusher head from the desiredcircular rotational path that, in turn, may result from changes in thetype, flow rate or volume of material within the crushing zone (betweenthe crushing shells) and/or the shape and in particular imperfections orwear of mantle and concave.

According to a second aspect of the present invention there is providedan inertia cone crusher comprising a pulley as claimed herein.

According to a third aspect of the present invention there is providedan inertia crusher comprising: a frame to support an outer crushingshell; a crusher head moveably mounted relative to the frame to supportan inner crushing shell to define a crushing zone between the outer andinner crushing shells; a drive transmission mechanism as describedherein and a torque reaction pulley as described and claimed herein.

The present torque reaction pulley is advantageous to be dynamicallyresponsive to changes in the rotational path and/or the angular velocityof the mass body and in particular a change in the rotational motion ofthe crusher head about the gyration axis and/or a rotational speed ofthe crusher head. This in turn causes the change in torque within thedrive transmission. The present torque reaction pulley thereforeprovides a flexible linkage to accommodate undesired and unpredictedtorsion created by rotation of the mass body.

BRIEF DESCRIPTION OF DRAWINGS

A specific implementation of the present invention will now bedescribed, by way of example only, and with reference to theaccompanying drawings in which:

FIG. 1 is a cross-sectional view through an inertia cone crusheraccording to one specific implementation of the present invention;

FIG. 2 is a schematic side view of selected moving components within theinertia crusher of FIG. 1 including in particular a crushing head, anunbalanced weight and a drive transmission;

FIG. 3 is a cross-sectional perspective view of a torque reaction pulleybeing a drive input component of the crusher of FIG. 1;

FIG. 4 is a further cross-sectional view of the pulley of FIG. 3;

FIG. 5 is a cross-sectional perspective view of a further specificimplementation of an elastically deformable component forming a part ofa drive input pulley;

FIG. 6 is a further cross-sectional perspective view of a region of theelastically deformable component of FIG. 5.

FIG. 7 is a further specific implementation of a torque reaction pulleyhaving an elastically deformable component positioned between selecteddrive transmission components within the pulley.

DETAILED DESCRIPTION OF PREFERRED EMBODIMENT OF THE INVENTION

FIG. 1 illustrates an inertia cone crusher 1 in accordance with oneembodiment of the present invention. The inertia crusher 1 comprises acrusher frame 2 in which the various parts of the crusher 1 are mounted.Frame 2 comprises an upper frame portion 4, and a lower frame portion 6.Upper frame portion 4 has the shape of a bowl and is provided with anouter thread 8, which cooperates with an inner thread 10 of lower frameportion 6. Upper frame portion 4 supports, on the inside thereof, aconcave 12 which is a wear part and is typically cast from a manganesesteel.

Lower frame portion 6 supports an inner crushing shell arrangementrepresented generally by reference 14. Inner shell arrangement 14comprises a crushing head 16, having a generally coned shape profile andwhich supports a mantle 18 that is similarly a wear part and typicallycast from a manganese steel. Crushing head 16 is supported on apart-spherical bearing 20, which is supported in turn on an innercylindrical portion 22 of lower frame portion 6. The outer and innercrushing shells 12, 18 form between them a crushing chamber 48, to whichmaterial that is to be crushed is supplied from a hopper 46. Thedischarge opening of the crushing chamber 48, and thereby the crushingperformance can be adjusted by means of turning the upper frame portion4, by means of the threads 8,10, such that the vertical distance betweenthe shells 12, 18 is adjusted. Crusher 1 is suspended on cushions 45 todampen vibrations occurring during the crushing action.

The crushing head 16 is mounted at or towards an upper end of a mainshaft 24. An opposite lower end of shaft 24 is encircled by a bushing26, which has the form of a cylindrical sleeve. Bushing 26 is providedwith an inner cylindrical bearing 28 making it possible for the bushing26 to rotate relative to the crushing head shaft 24 about an axis Sextending through head 16 and shaft 24.

An unbalance weight 30 is mounted eccentrically at (one side of) bushing26. At its lower end, bushing 26 is connected to the upper end of adrive transmission mechanism indicated generally by reference 55. Drivetransmission 55 comprises a first upper torsion bar 5 having a firstupper end 7 and a second lower end 9. The first end 7 is connected to alowermost end of bushing 26 via a race 31 whilst second end 9 is mountedin coupled arrangement with a drive shaft 36 rotatably mounted at frame6 via a bearing housing 35. A second lower torsion bar 37 is drivablycoupled to a lower end of drive shaft 36 via its first upper end 39. Acorresponding second lower end 38 of second torsion bar 37 is mounted ata drive pulley indicated generally by reference 42. An upper balancedweight 23 is mounted to an axial upper region of drive shaft 36 and alower balanced weight 25 is similarly mounted at an axial lower regionto drive shaft 36. According to the specific implementation, drive shaft36, bearing housing 35, first and second torsion bars 5, 37 and pulley42 are aligned coaxially with one another, main shaft 24 and crushinghead 16 so as to be centred on axis S. Drive pulley 42 mounts aplurality of drive V-belts 41 extending around a corresponding motorpulley 43. Pulley 42 is driven by a suitable electric motor 44controlled via a control unit 47 that is configured to control theoperation of the crusher 1 and is connected to the motor 44, forcontrolling the RPM of the motor 44 (and hence its power). A frequencyconverter, for driving the motor 44, may be connected between theelectric power supply line and the motor 44. Pulley 42 comprises atorque reaction coupling indicated generally by reference 32 having atleast one component being configured to deform and/or displaceelastically in response to changes torque changes as described in detailbelow.

According to the specific implementation, drive mechanism 55 comprisesfour CV joints at the regions of the respective mounting ends 7 and 9 ofthe first torsion bar 5 and the respective ends 39, 38 of the secondtorsion bar 37. Accordingly, the rotational drive of the pulley 42 bymotor 44 is translated to bushing 26 and ultimately unbalanced weight 30via intermediate drive transmission components 5, 36 and 37.Accordingly, pulley 42 may be regarded as a drive input component ofcrusher 1. Pulley 42 is centred on a generally vertically extendingcentral axis C of crusher 1 that is aligned coaxially with shaft andhead axis S when the crusher 1 is stationary.

When the crusher 1 is operative, the drive transmission components 5,36, 37 and 42 are rotated by motor 44 to induce rotation of bushing 26.Accordingly, bushing 26 swings radially outward in the direction of theunbalance weight 30, displacing the unbalance weight 30 away fromcrusher vertical reference axis C in response to the centrifugal forceto which the unbalance weight 30 is exposed. Such displacement of theunbalance weight 30 and bushing 26 (to which the unbalance weight 30 isattached), is achieved due to the motional freedom of the CV joints atthe various regions of drive transmission 55. Additionally, the desiredradial displacement of weight 30 is accommodated as the sleeve-shapedbushing 26 is configured to slide axially on the main shaft 24 viacylindrical bearing 28. The combined rotation and swinging of theunbalance weight 30 results in an inclination of the main shaft 24, andcauses head and shaft axis S to gyrate about the vertical reference axisC as illustrated in FIG. 2 such that material within crushing chamber 48is crushed between outer and inner crushing shells 12, 18. Accordingly,under normal operating conditions, a gyration axis G, about whichcrushing head 16 and shaft 24 will gyrate, coincides with the verticalreference axis C.

FIG. 2 illustrates the gyrating motion of the central axis S of theshaft 24 and head 16 about the gyration axis G during normal operationof the crusher 1. For reasons of clarity, only the rotating parts areillustrated schematically. As the drive shaft 36 and torsion rods 5 and37 are rotated by the induced rotation of drive input pulley 42, theunbalance weight 30 swings radially outward thereby tilting the centralaxis S of the crushing head 16 and the shaft 24 relative to the verticalreference axis C by an inclination angle i. As the tilted central axis Sis rotated by the drive shaft 36, it will follow a gyrating motion aboutthe gyration axis G, the central axis S thereby acting as a generatrixgenerating two cones meeting at an apex 13. A tilt angle α, formed atthe apex 13 by the central axis S of head 16 and the gyration axis G,will vary depending on the mass of the unbalance weight 30, the RPM atwhich the unbalance weight 30 is rotated, the type and amount ofmaterial that is to be crushed, the DO setting and the shape profile ofthe mantle and concave 18, 12. For example, the faster the drive shaft36 rotates, the more the unbalance weight 30 will tilt the central axisS of the head 16 and the shaft 24. Under the normal operating conditionsillustrated in FIG. 2, the instantaneous inclination angle i of the head16 relative to the vertical axis C coincides with the apex tilt angle αof the gyrating motion. In particular, when the drive transmissioncomponents 5, 36, 37 and 42 are rotated the unbalanced weight 30 isrotated such that the crushing head 16 gyrates against the material tobe crushed within the crushing chamber 48. As the crushing head 16 rollsagainst the material at a distance from the periphery of the outercrushing shell 12, central axis S of crushing head 16, about which axisthe crushing head 16 rotates, will follow a circular path about thegyration axis G. Under normal operating conditions the gyration axis Gcoincides with the vertical reference axis C. During a completerevolution, the central axis S of the crushing head 16 passes from0-360°, at a uniform speed, and at a static distance from the verticalreference axis C.

However, the desired circular gyroscopic precession of head 16 aboutaxis C is regularly disrupted due to many factors including for examplethe type, volume and non-uniform delivery speed of material within thecrushing chamber 48. Additionally, asymmetric shape variation of thecrushing shells 12, 18 acts to deflect axis S (and hence the head 16 andunbalanced weight 30) from the intended inclined tilt angle i. Suddenchanges from the intended rotational path of the main shaft relative toaxis G and speed of the unbalanced weight 30 manifest as substantialexaggerated dynamic torsional changes that are transmitted into thedrive transmission components 5, 36, 37 and 42. Such dynamic torque canresult in accelerated wear, fatigue and failure of the drivetransmission 55 and indeed other components of the crusher 1.

Torque reaction coupling 32, comprises at least one elastic componentconfigured to deform elastically in response to receipt of the dynamictorque resultant from the undesired and uncontrolled movement and speedof unbalanced weight 30. In particular, coupling 32 is adapted to beself-adjusting via twisting, radial and/or axial expansion andcontraction as torque is transmitted through the transmission 55.Accordingly, the reaction torque resultant from the exaggerated motionof unbalanced weight 30 is dissipated by coupling 32 and is inhibitedand indeed prevented from propagation within the drive transmission 55.Torque reaction coupling 32 is configured to receive, store and at leastpartially return torque to components of the drive transmission 55 suchas in particular bushing 26 and unbalanced weight 30. Accordingly,unbalanced weight 30 via coupling 32 is suspended in a ‘floating’arrangement relative to parts of the drive transmission 55. That is,coupling 32 enables a predetermined amount of change in the tilt angle iof weight 30 in addition to changes in the angular velocity of weight 30relative to the corresponding rotational drive of components 36, 37 and42

Referring to FIGS. 3 and 4, the drive pulley 42 comprises a radiallyoutermost race 69 having a series of grooves 51 to partially accommodatethe V-belts 41 (FIG. 1) configured to drive rotation of race 69. Aradially inner race 67 defines a socket 68 to receive the lower end 38of lower torsion bar 37. An inner bearing assembly, comprising bearings70 and bearing raceways 71, is mounted radially outside inner race 67and secured in position via an upper mounting disc 73 and a lowermounting disc 74. An adaptor shaft indicated generally by reference 81comprises a radially outward extending axially upper cup portion 84non-moveably attached to a lower region 83 of inner race 67. Adaptorshaft 81 also comprises a radially outward extending flange 85 providedat a lowermost end of shaft 81. An outer bearing assembly, comprisingbearings 88 and bearing raceways 87, is positioned radially between thegrooved radially outer race 69 and a bearing housing 72 that ispositioned radially between the two bearings assemblies 87, 88 and 70,71. Accordingly, the outer grooved race 69 is capable of independentrotation relative to the inner race 67 via the respective bearingassemblies 70, 71 and 87, 88.

The flexible torsion coupling 32 is positioned in the drive transmissionpathway between the grooved pulley race 69 and the inner race 67 viaadaptor shaft 81. According to the specific implementation, coupling 32comprises a modular assembly formed from deformable elastomeric ringsand a set of intermediate metal disc springs. In particular, a firstannular upper elastomer ring 78 mounts at its lowermost annular face afirst half of a disc spring 79. A corresponding second lower annularelastomer ring 77 similarly mounts at its upper annular face a secondhalf of the disc spring 80 to form an axially stacked assembly in whichthe metal disc spring 79, 80 separates respective upper and lowerelastomeric rings 78, 77. Rings 78, 77 are formed from a relatively softelastomeric material that is deformed and in particular twistedinternally (by around 15 to 20°) during an initial preloading of thecrusher when motor is operational and torque is transmitted through thecoupling 32. A first upper annular metal flange 76 is mounted at anupper annular face of the upper elastomer ring 78 and a correspondingsecond lower metal flange 89 is attached to a corresponding axiallylower face of the lower elastomer ring 77. Upper flange 76 is attachedat its radially outer perimeter to a first upper adaptor flange 75formed as a thin plate of a steel material. Flange 75 is secured at itsradially outer perimeter to a lower annular face of the grooved beltrace 69. Accordingly, adaptor flange 75 and coupling flange 76 provideone half of a mechanical coupling between the grooved V belt race 69 andthe flexible coupling 32. Similarly, a second lower adaptor flange 82,(also formed from as a thin plate of a steel material) is mounted to thelower coupling flange 89 at a radially outer region and is mounted toadaptor shaft flange 85 at a radially inner region. Accordingly, adaptorflange 82 provides a second half of the mechanical connection betweenflexible coupling 32 and inner race 67 (via adaptor shaft 81). Each ofthe elastomeric components 78 and 77 are configured to elasticallydeform in response to torsional loading in a first rotational directiondue to the drive torque and in the opposed rotational direction by thereaction torque. Adaptor flanges 75 and 82 are specifically configuredphysically and mechanically to be stiffer in torsion relative tocomponents 77, 78, but to be deformable axially so as to provide axialfreedom and to allow components 78, 77 to flex in response to the torqueloading.

Flexible coupling 32 is demountably interchangeable at pulley 42 via aset of releasable connections. In particular, upper coupling flange 76is releasably mounted to adaptor flange 75 via attachments bolts 97 andlower coupling flange 89 is releasably attached to adaptor flange 82 viacorresponding attachment bolts 50. Similarly, adaptor flange 75 isreleasably mounted to outer race 69 via a set of attachment bolts 52.Additionally, lower adaptor flange 82 is releasably attached to theadaptor shaft flange 85 via releasable attachment bolts 98.

Adaptor shaft 81 is interchangeably mounted at race lower region 83 viaa set of attachment threaded bolts 53 received with threaded bores 106extending axially into race 67 from lower region 83. Accordingly,coupling 32 is interchangeable (mountable and demountable) at pulley 42via some or all of the releasable attachment components 52, 97, 50, 98and 53. Such a configuration is advantageous to selectively adjust thetorque reaction characteristic of pulley 42 as desired to suit forexample different types of material to be processed, different materialfeed flow rates, the status and integrity of the inner and outercrushing shells 18, 12 and the speed or power drawer of the motor thatdrives the drive transmission 55. Additionally, the material ofelastomeric rings 77, 78 and flanges 75 and 82 may be selected toachieve the desired deformation characteristic with regard to theannular range of twist of coupling 32 and the axial displacementprovided by flange 82.

In the mounted position at pulley 42, the elastomeric components 78, 77(in addition to the metal disc spring 79, 80) are configured to deformradially and axially via twisting, axial and radial compression andexpansion in response to the driving and reaction torques. Coupling 32,is accordingly configured to dissipate the undesired reaction torquecreated by the change in the tilt angle α and the non-circular orbitingmotion of the unbalanced weight 30. In particular, coupling 32 isconfigured specifically to absorb and dissipate torque.

FIGS. 5 to 6 illustrate further embodiments of torque reaction coupling32 forming a component part of pulley 42. According to the furtherembodiment of FIGS. 5 and 6, the elastic deformation is provided by aplurality of radially extending spokes 58 that are capable of distortingand deflecting in a circumferential direction (by rotation) and hence torespond to the change in torque induced by the motion of unbalancedweight 30. Each spoke is separated circumferentially and radially fromneighbouring spokes 58 by gap regions 104 that allow each spoke 58 toflex in the circumferential and radial directions. In particular,coupling 32 comprises a stack 54 of metal discs 60 that each comprises aradially outermost perimeter region 56 and a radially innermost region57. Spokes 58 extend between regions 56 and 57 with each spoke extendingalong a segment of a spiral having a generally arcuate curved shapeprofile. Each spoke 58 extends radially inward from a perimeter collar105 and is terminated at its radially innermost end by a mounting hub101. A plurality of mounting flanges 59 project radially outward fromouter collar 105 of an uppermost disc 60 of the stack 54. It is notedthat only a portion of the stack 54 is illustrated and a correspondinglowermost disc (not shown) of the stack comprises corresponding flanges59.

Each of the discs 60 are arranged in pairs in the axial direction withneighbouring discs of a pair each connected outwardly towards perimeterregion 56 or innermost region 57. A polarity of bores 99 extend througheach collar 105 with an attachment bolt 100 coupling two discs 60 of apair. The discs 60 of a corresponding adjacent pair of the stack 54 arecoupled at respective inner regions 57 via mounting hubs 101. Inparticular, each hub 101 of adjacent discs 60 are coupled via a mountingpin 102 received within a corresponding bore 103 extending axiallythrough each hub 101. Accordingly, stack 54 comprises respective pairsof discs 60 that are connected together in an alternating sequence inthe axial direction via their outer regions 56 and inner regions 57. Theaxial endmost discs 60 are accordingly attached to a mounting flange(not shown) corresponding to respective upper and lower metal couplingflanges 76, 89 with the discs 60 sandwiched axially between the upperand lower flanges (or plates). With the stack 54 mounted in position atpulley 42 and uppermost disc 60 of the stack is attached to outer race69 and a lowermost disc 60 of the stack is attached to inner race 67.Accordingly, both the drive and the reaction torque are transmittedthrough discs 60 and in particular spokes 58 that are configured todeflect in the circumferential direction (by rotation) such that outercollar 105 is capable moves radially inward and outward relatively toinner race 67 (and axis C). As will be appreciated, the number, shapeand configuration of spokes 58 may be selected accordingly to furtherembodiments to suit the elastic deformation characteristic of thecoupling 32.

According to further embodiments, coupling 32 being positioned in thedrive transmission between outer race 69 and inner race 67 and maycomprise a spring, and in particular a torsion spring, a coil spring, ahelical spring, a fluid (or liquid) spring, a torsion disc spring or acompression spring.

Also, the deformable coupling 32 may be positioned at different regionsof pulley 42 and in particular intermediate in the drive transmissionpathway between outer race 69 and inner race 67 including for examplebetween inner race 67 and bearing housing 72; inner race 67 and adaptorshaft 81; adaptor shaft 81 and outer race 69 or a combination of thesedifferent positions. In particular, the torsional responsive pulley 42is described according to a further embodiment in which deformablecoupling 32 is positioned between inner race 67 and bearing housing 72.Being similar to the embodiment of FIGS. 3 and 4, coupling 32 comprisesa modular assembly having first and second elastomeric rings 140, 143secured between respective upper and lower mounting plates 141, 142. Ametal disc spring 146 partitions the upper and lower elastomeric rings140, 143 and is configured to allow a degree of independent rotationalmotion of rings 140, 143 resulting from torque induced by the motion ofunbalanced weight 30. Lower plate 142 is mounted at its radially innerregion 144 to a radially outward extending flange 145 projecting frombearing housing 72 as described with reference to FIGS. 3 and 4.Similarly, a radially inner region 144 of upper plate 141 is coupled toa radially outward extending flange 150 projecting from an upper regionof inner race 67 that supports lower torsion rod 37 as described withreference to FIGS. 3 and 4. Accordingly, drive and reaction torque istransmitted between bearing housing 72 and inner race 67 via flexiblecoupling 32. Accordingly, the undesirable reaction torque is dissipateddynamically by the rotational twisting of elastomer rings 140, 143 andthe movement of the intermediate disc spring 146.

1. A torque reaction pulley mountable at an inertia crusher to form partof a drive transmission mechanism for rotational drive of an unbalancedmass body within the crusher, the pulley comprising: a drive inputportion connectable to a motor to provide rotational drive to thepulley; a drive output portion connectable to the mass body to transmitthe rotational drive to the mass body; and an elastic component formednon-integrally with the drive input and output portions and having afirst part anchored in coupled connection with the drive input portionand a second part anchored in coupled connection with the drive outputportion so as to be positioned in the drive transmission pathwayintermediate the drive input and output portions, the elastic componentbeing configured to transmit a torque to the mass body and todynamically displace and/or deform elastically in response to a changein the torque resultant from rotation of the mass body within thecrusher so as to dissipate the change in the torque at the crusher. 2.The pulley as claimed in claim 1, wherein the elastic component isattached to the drive input and output portions via releasableattachments such that the elastic component may be mounted and decoupledfrom the drive input and output portions.
 3. The pulley as claimed inclaim 1, wherein the elastic component is mounted at one end of thepulley.
 4. The pulley as claimed in claim 2, wherein at least parts ofthe attachments are positioned externally at the pulley.
 5. The pulleyas claimed in claim 1, wherein the elastic component is connectedindirectly to the drive output portion via at least one drive componentforming a part of the pulley and configured to transmit the torque. 6.The pulley as claimed in claim 1, wherein the elastic component isconnected indirectly to the drive input portion via at least one drivecomponent forming a part of the pulley and configured to transmit thetorque.
 7. The pulley as claimed in claim 1, wherein the drive inputportion includes an annular belt support component arranged to mount andpositionally support a belt drive to extend at least partially aroundthe belt support component.
 8. The pulley as claimed in claim 1, whereinthe drive output portion includes a race having an internally extendingsocket capable of mounting one end of a torsion bar or drive shaftdemountably connectable to the pulley.
 9. The pulley as claimed in claim1, further comprising a first adaptor flange coupled between andconnecting the drive input portion and the elastic component.
 10. Thepulley as claimed in claim 9, further comprising a second adaptor flangecoupled between and connecting the drive output portion and the elasticcomponent.
 11. The pulley as claimed in claim 10, further comprising anadaptor shaft extending between and connecting the second adaptor flangeand the drive output portion.
 12. The pulley as claimed in claim 1,wherein the elastic component includes at least one elastomericcomponent configured to twist in response to the transmission of thetorque through the pulley.
 13. The pulley as claimed in claim 1, whereinthe elastic component at least one disc having spokes configured todeform via twisting about a rotational axis of the pulley in response totransmission of the torque through the pulley.
 14. The pulley as claimedin claim 13, further comprising a plurality of discs stacked on top ofone another via interconnecting members such that the spokes arearranged in series and/or in parallel in the drive transmission pathwayintermediate to the drive input and output portions.
 15. An inertia conecrusher comprising the pulley of claim 1.